Brake mechanism for control of vertical motion of a vertically aligned adjustable drain tube

ABSTRACT

A portable vehicle fluid drain device is disclosed. The device includes a vertical drain tube which supports a vehicle fluid drain bowl. The drain tube is manually adjusted to an elevated position, latched in place while the vehicle fluid is drained, and unlatched to descend at a rate less than that of free fall due to the use of a friction brake. The friction force imparted by the brake on the drain tube is adjusted by rotating a wing nut on a carriage bolt to squeeze the inner edges of two wishbone arms against the drain tube. A method of using a vehicle fluid drain device with a brake and a self-latching mechanism is disclosed.

TECHNICAL FIELD

The present invention relates to mechanical devices used to hold andrelease vertically aligned vehicle fluid drain tubes. More particularly,the present invention relates to such mechanical devices used to holdand release vehicle fluid drain tubes to allow gravity driven axialmovement of the drain tube relative to the mechanism. The drain tube isused to position a drain bowl under a vehicle fluid drain to catchdraining fluids. The drain tube provides a fluid channel for drainingthe contents of the drain bowl to a fluid reservoir.

BACKGROUND ART

Self-latching mechanisms for holding a cylindrical item are well known.This is not surprising since cylindrical shapes are common as eitherconduits or as structural elements. The cylindrical shape is common dueto its ease of manufacture and favorable mechanical properties.

Typically, the self-latching mechanisms are adapted to grab and hold thecylindrical item to prevent gravity induced downward movement of thecylindrical item. The self-latching mechanisms are adapted to allow theuser to release the cylindrical item from the self-latching mechanism.Examples of such self-latching mechanisms include U.S. Pat. No. 836,303granted on Nov. 20, 1906, to Christensen.

The Christensen patent describes an automatic locking collar which maybe adjusted either up or down on a cylindrical item. The automaticlocking collar will lock automatically in any position against furthermovement in one direction on the cylindrical item. The Christensenpatent also teaches that the collar may be fixed and the cylindricalitem may be moved up and down at will through the collar until thecollar locks automatically against further movement of the cylindricalitem in one direction.

The Christensen locking mechanism is a latch plate with a cut-outslightly larger than the cylindrical item. When the latch plate isreleased, the latch plate rotates down and the inside edge of thecut-out in the latch plate contacts the cylindrical item. If the collaris fixed, the force of gravity moves the cylindrical item downward andcauses the latch plate to rotate around an axis in order to move thecontacting edge of the latch plate further toward the center of thecylindrical item. Since the latch plate and the cylindrical item cannotoccupy the same space, the downward movement of the cylindrical itemcontinues briefly until the interference between the latch plate and thecylindrical item binds the cylindrical item in place.

In order to free or release the cylindrical item, the latch plate isrotated about its pivot so as to disengage from the cylindrical item.The cylindrical item is released when the latch plate is rotated up andout of the way, in order to free the cylindrical item. The latch platein many self-latching mechanisms can be rotated out of the way eitherdirectly through use of a handle, or indirectly by lifting thecylindrical item up to push the latch plate up. Since such a latch plateis basically a one-way brake, by reason of the servo action of itsengagement, a single latch plate will be used to prevent motion in onlyone direction.

The prior art contains a wide variety of variations on the self-latchingmechanism in a variety of applications.

U.S. Pat. No. 1,494,022, issued on May 13, 1924, to Roberson teaches adevice for clamping a sucker rod to hold the rod while it is beingassembled and inserted into a well. The Roberson device uses a latchplate which is mounted on a hinged plate that straddles the sucker rodas it passes through a cylindrical void slightly larger than the suckerrod. The hinged plate can be rotated so the latch plate does notinterfere with the movement of the sucker rod. The hinged plate can alsobe rotated toward the sucker rod so that contact with the latch platewill bind the sucker rod against the inner wall of the cylindrical void.

U.S. Pat. No. 2,051,969, issued on Aug. 25, 1936, to Shastock isdirected to an automatic tube adjuster for telescoping tubes. TheShastock device uses a latch plate with a cut-out through which thecylindrical item passes. The Shastock device uses a spring toautomatically move the latch plate into contact with the cylindricalitem in lieu of using the weight of the handle to rotate the latch plateinto position.

Self-latching mechanisms have been used since at least 1906 in a widevariety of applications, and yet there is a significant limitation insuch prior art mechanisms. The limitation is that the prior artmechanisms provide only limited control over the motion of thecylindrical item relative to the self-latching mechanism. The bind andrelease states of the latch are two polar extremes. Either thecylindrical item is totally bound and cannot move at all, or thecylindrical item is totally released and thus free to fall through thelatch mechanism without any impediment to travel.

This shortcoming in prior art devices is not serious if the use is onein which the user is holding the cylindrical item to position it. If theuser is holding the cylindrical item, it cannot fall when the latchplate is released. Examples include precise positioning of a dress formto a selected height, or positioning the tilt of a drafting table. Oncesuch adjustments are made, readjustments are not required until there isa new use for the dress form or the drafting table. In suchcircumstances it is not unduly burdensome to require the user tomomentarily support the weight of the cylindrical item and any loadattached to the cylindrical item.

Other applications for self-latching mechanisms may require morefrequent adjustments. For example, a movie screen support will be set upand put away with each use. In this case the cylindrical object willtypically have an extended position and a retracted position. Whilethere may be some range of desired extended positions, the retractedposition is fully retracted so the movie screen can be folded andstored. When the desired position of the retracted position is fullyretracted, it is foreseeable that the user will release the latchmechanism and allow the cylindrical object to travel all the way backuntil it hits a mechanical stop that prevents further retraction. Sincethe latch mechanism lacks an intermediate state between fully latchedand totally free, the cylindrical item if not manually restrained,accelerates under the force of gravity until hitting the mechanicalstop.

The lack of intermediate states between being fully bound and being freeto fall is not a problem if the latch mechanism is used in a device inwhich the cylindrical item can free fall without causing any harm. Whenthe cylindrical item crashes into the mechanical stop, there will benoise; and the sudden movement and the noise may surprise the user. Thissituation is usually tolerable for most devices; and in some cases, suchsituations can be mitigated by adding springs or cushions to themechanical stop to soften the impact and reduce the noise. However, asdescribed below free fall is not suitable for all applications oflatches.

SUMMARY OF THE INVENTION

Thus the prior art has examples of ways to bind and hold a cylindricalitem in a fixed position and then fully release the cylindrical item.This is tolerable for some applications, however, some applications thatwould use a latch mechanism would preferably restrain the rate ofdescent of the cylindrical item.

One such application is a latch mechanism for a portable oil drain unit.The oil drain unit has a vertical drain tube that is adjusted from adown position to an elevated position just under the undercarriage of avehicle. The drain tube is adjusted up and down with each use of theportable oil drain unit. The drain tube has a travel range of more thantwo feet and supports a drain bowl which may contain tools or vehicleparts. A restraint on the rate of acceleration is important for thisapplication because the drain tube and the supported heavy drain bowlcan accelerate quite a bit while traveling more than two feet. Theadverse consequences of sudden rapid downward movement of heavy itemscould include substantial noise, risk of contact of items connected tothe drain tube item with other non-moving items, including splashing ofvehicle fluids onto nearby items, and increased wear through shock,vibration, and distortion of material in the portions of the apparatusthat collide as part of the physical stop.

A restraint that cannot be easily adjusted is only a partial cure.Ideally, the amount of resistance or braking force that is exerted canbe varied. The ability to vary the braking force would not necessarilyrequire precise control over the amount of braking force that is appliedduring the descent of the drain tube. Such precision is not required inorder to achieve the objectives of reducing the speed of travel towithin acceptable limits. The user retains the ability to release theself-latching mechanism and cause the latch plate to engage the side ofthe drain tube to stop the descent if the speed slowly builds toundesired levels.

However it would be preferable for the braking unit to be adjustable tocompensate for: 1) heavier loads, 2) the presence of lubricants whichreduce the effectiveness of the braking force or, 3) wear on the brakesor the surface of the drain tube that reduce the effectiveness of thebraking force. Additionally, some users may prefer a quick butcontrolled descent and other users may prefer a much slower descent. Ifthe device is to serve the needs of many users, then it is preferablethat users be able to make adjustments to their individual preferences.To be most convenient, the adjustment should be designed so thatadjustment can be made by hand without any special tools.

Ideally, the brake for controlling the fall of the drain tube should bedesigned so that it can be integrated with latch mechanisms to simplifythe construction and use of the brake.

In addition to being inexpensive to manufacture, simple to use, theideal brake should be easy to maintain and should not impede themobility of the device to which the brake is added. Thus, the idealbrake should not use pneumatic, electronic, or electric forces whichlimit the mobility of a mobile unit that used the brake.

Therefore it is an object of the present invention to provide a brake tobe used to selectively control the rate of acceleration of a verticallyaligned stationary drain tube from no acceleration to essentially theacceleration of gravity.

It is another object of the present invention to provide a brake for avertically aligned drain tube that can be adjusted to compensate forvariations in weight of associated load, wear on the brake surface, wearon the surface of the drain tube, and presence of lubricants whichreduce friction braking.

It is an additional object of the present invention to provide a braketo control vertical movement of a vertically aligned drain tube whichcan be adjusted without tools to facilitate adjustments for changes inweight of the load supported by the drain tube, or to accommodatepreferences of individual users for the amount of braking to be applied.

It is also an object of the present invention to provide a combinationof a latch mechanism and a brake for controlling the vertical movementof a vertically aligned drain tube.

It is yet another object of the present invention to provide aself-latching mechanism with a brake such that the mechanism can beoperated with one hand after the brake adjustment is set to the desiredsetting.

It is yet an additional object of the present invention to provide aself-latching mechanism with a brake which can be operated without theuse of electricity, pneumatics, or hydraulics and which is inexpensiveto manufacture and maintain.

It yet still another object of the present invention to provide aself-latching mechanism with a brake that can be used repetitivelywithout fatigue to the user from operation of the brake.

It yet still further an object of the present invention to provide aself-latching mechanism in which the brake adjustment does not requirethe user to squeeze the brake adjustment to maintain the desired brakingforce.

Other objects and advantages of the present invention will becomereadily apparent from the description provided.

In accordance with the present invention, a brake for use in restrainingthe downward acceleration of a vertically aligned drain tube is providedby a motion resisting contact area which is presses against the outerwall of the drain tube to resist downward motion. The resistance todownward motion is varied by a brake adjustment. The preferredembodiment contains a brake and brake adjustment which are integratedinto a handle for a self-latching mechanism.

The present invention includes a method of draining a vehicle fluid froma vehicle into a drain bowl mounted on a drain tube which is moveablerelative to a fluid chamber. The steps include 1) placing the drain bowland drain tube under the vehicle fluid drain, 2) raising the drain bowlwith the drain tube to an extended position close to and below thevehicle fluid drain, 3) latching the drain tube to hold the drain bowlin position, 4) draining the vehicle fluid from the vehicle into thedrain bowl, 5) releasing the drain tube to permit the drain bowl and thedrain tube to retract from the extended position, and 6) applying abraking force to the drain tube to limit the acceleration of the drainbowl and drain tube as the drain tube retracts from the extendedposition. The braking force may be adjusted to provide resistanceappropriate to conditions and user preference.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will be more fully understood by reference to thefollowing detailed description when considered in conjunction with thefollowing drawings wherein like reference numbers denote the same partsshown throughout the several FIGURES in which:

FIG. 1 shows a side view of a portable oil drain with its drain tubeextended to position the oil bowl under an elevated vehicle and apartial cutaway of the drain tank to show the reservoir of waste oilcontained within;

FIG. 2 shows an exploded view of the preferred embodiment of the presentinvention which combines a brake with a brake adjustment and aself-latching mechanism;

FIG. 3 shows a top down view of the preferred embodiment of a brake witha brake adjustment and a self-latching mechanism when the handleassembly is rotated into a position that places the leading edge of thelatch plate over the cylindrical void of the pivot plate;

FIG. 4 shows a top down view of an alternate embodiment of the presentinvention which uses a floating latch plate with a circular cut-out andincludes a partial cutaway of one of the wishbone arms to reveal thedifference in size between the latch tab and the arm slot;

FIG. 5 shows a side view of a floating latch plate with a circularcut-out that is aligned at an oblique angle with respect to the surfaceof the top surface of the floating latch plate;.

FIG. 6 shows a side view of another alternate embodiment of the presentinvention which uses a floating latch plate that is not part of apivotally mounted handle assembly and uses a brake mechanism which isnot part of a pivotally mounted handle assembly (best shown in FIG. 8);

FIG. 7 shows a top view of the floating latch plate from FIG. 6.;

FIG. 8 shows a top view of the embodiment shown in FIG. 6 but with thefloating latch plate removed to afford an unobstructed view of the brakemechanism thumbscrew and conical sleeve which serves as a wedge shapedobject;

FIG. 9 shows an enlarged top view of the thumbscrew, wedge shapedobject, and related elements.;

FIG. 10 shows a top view of another embodiment of the present inventionin the latched position which uses a wedge shaped void on the pivot sideof the drain tube to bind the drain tube and a threaded assembly tosqueeze the handle arms to serve as motion resisting surfaces;

FIG. 11 shows a side view of the embodiment shown in FIG. 10;

FIG. 12 shows a side view of the embodiment shown in FIG. 10 but withthe handle arms in the unlatched position;

FIG. 13 shows a sectional view of FIG. 12 to highlight the position ofthe unlatched drain tube relative to the wedge shaped void;

FIG. 14 shows a top view of another embodiment of the present inventionthat uses a ball constrained to travel in a channel as part of the latchmechanism combined with a braking mechanism controlled by a threadedassembly which also serves as part of the pivotal mounting of the handlearms; and

FIG. 15 shows a side view of the embodiment shown in FIG. 14 but withpartial cut away to show the position of the ball relative to the fixedelement with its concave channel, the pin serving as the upperrestraint, the second pin serving as the lower restraint, and theinteraction between the drain tube and the ball.

BEST MODE FOR CARRYING OUT THE INVENTION AND ITS INDUSTRIALAPPLICABILITY

The following detailed description is divided into sections which havesection titles to indicate the general nature of the informationcontained in that section. The sections and their titles are intendedsolely to assist in the organization and to assist the reader. The useof sections and section titles is not intended to indicate thatinformation suggested by any one title is not contained in any othersection.

The Environment for Use of the Present Inventions

The environment for use of the present invention is shown in FIG. 1.FIG. 1 shows a side view of a portable oil drain 100 which is used in aservice or repair facility for vehicles. In use, the portable oil drain100 is placed under an automobile 102, which has been elevated and issupported by a lift symbolized by reference number 104. Mobility of theportable oil drain 100 is facilitated by a set of wheels 106 connectedto the base of the portable oil drain 100. After positioning theportable oil drain 100 under the automobile 102 the user lifts a drainbowl 108 to a desired height under the oil filter, drain plug, or othervehicle fluid drain port underneath the automobile 102. Once the drainbowl 108 is in position, the user lets go of the drain bowl 108. A draintube 110 that connects the drain bowl 108 to the rest of the portableoil drain 100 descends very slightly through a self-latching mechanism112 until the self-latching mechanism 112 acts to stop and hold thedrain tube 110 against the force of gravity acting upon the combinedweight of the drain tube 110, the drain bowl 108, and the contents ofthe drain bowl (e.g., one or more used oil filters).

With the drain bowl 108 in the elevated position, the user drains theoil from the automobile 102 into the drain bowl 108, through the draintube 110, and into a drain tank 114 having a cover 115 and which cancontain a reservoir of waste oil 116 left over from several previous oilchanges. After the oil has been drained, the user lifts a release handle118 to release the self-latching mechanism 112.

Before the present invention, the drain tube 110, would free fall uponrelease, and would stop when the drain bowl 108 struck the rest of theportable oil drain 100 or the drain tube 110 hit a mechanical stop inthe drain tank 114. Either way, there would be a sudden impact of thedrain bowl 108 and its contents upon reaching bottom. This suddenmovement and impact would have the undesirable effects of noise,possible splatter of residual oil from the drain bowl 108, andadditional wear and tear upon the portable oil drain 100 from therepeated impacts.

The free fall could be avoided by having the user hold the drain tube110 or drain bowl 108 to resist the force of gravity. Requiring use ofthe one free hand of the user is undesirable for several reasons.

First, having the user hold the descending drain bowl 108 would notserve any other useful purpose such as for precise positioning of thedrain bowl 108. Using hands to position the drain bowl 108 under theautomobile 102 is necessary due to variations of the position of thelift 104 and variations among automobile models of the position of theoil filter or drain plug under the automobile 102. However, the userdoes not need to position the drain bowl 108 on descent since theoptimal position is typically all the way down.

Second, the user may have only one free hand, with a wrench, rag or workorder in the other hand. The user is usually able to use two hands whilelifting the drain bowl 108 but may be disposed to use only one handduring descent of the drain bowl 108 and use that one hand for therelease handle 118. Grabbing the drain bowl 108 with the hand not on therelease handle 118, especially if the user waits until after the startof free fall to grab a moving bowl, could be awkward or uncomfortablefor the user.

Finally, requiring use of the second hand for slowing or controlling thedescent of the drain bowl 108 would usually require that the user putdown any tool or other carried object when the user simply wants to dropthe drain bowl 108 to the down position and drag the portable oil drain100 out from under the automobile 102. Therefore, ideally theself-latching mechanism 112 should be operable with one hand.

The situation illustrated in FIG. 1 has several aspects that make theaddition of a brake desirable. The weight of the drain bowl 108 whichmay contain tools or oil filters combined with a free fall of more thantwo feet generates a substantial amount of kinetic energy to be absorbedby the mechanical stop for the free falling drain tube 108.

The situation illustrated in FIG. 1. also illustrates several of thechallenges of adding a brake to a portable oil drain 100. One challengeis the virtual certainty that oil or other lubricants will get onto theoutside of the drain tube 110 or onto the brake. Lubricantssubstantially reduce mechanical friction which then substantiallydiminishes the braking force from any brake which uses mechanicalfriction.

The ideal brake would not use electric power for fear of sparks in anarea with petroleum products and other possible ignition sources. Inorder to maintain the portability of the portable oil drain 100, thebrake should not require connection to the repair shop's pneumatic airsupply, nor to an electric power source or a hydraulic supply. Also, thebrake mechanism should not greatly add to the cost, maintenance demands,or complexity of the portable oil drain 100.

The More Generalized Environment

Note that this description is using a specific fluid, oil, in order toillustrate the environment. Many other fluids are drained underneathraised automobiles including radiator fluid, transmission fluid, brakefluid, power steering fluid, and other hydraulic fluids. The use of thespecific fluid, oil, should be seen as illustrative and not limiting thescope of the present invention.

FIG. 1, depicts a typical situation in which a motor vehicle is servicedby lifting the automobile. In lieu of lifting the automobile, theportable drain unit can be located in a grease pit with the vehiclepositioned over the opening in the grease pit to give access to thevehicle fluid drains. In some service facilities, the volume of drainfluid collected makes it convenient to add additional tubing to move thedrained fluids to a larger stationary reservoir. Some grease pits mayuse rails rather than wheels to move the oil drain unit. The specificsrelating to 1) how the drain bowl 108 is moved laterally, 2) how thevehicle becomes elevated relative to the drain bowl 108, and 3) thelocation of the drain reservoir are presented in order to illustrate theenvironment for using the present invention but are not limitations onthe scope of the present invention.

The illustrative use of the present invention environment uses anautomobile as the vehicle. The term vehicle should be understood toinclude: automobiles, trucks, trailers for trucks, buses, locomotives,railroad cars, aircraft, and off-road vehicles whether for recreation,construction, or military use. Since the applicable use for the presentinvention includes draining vehicle fluids such as brake fluid whichoccur in vehicles such as truck trailers that do not have engines, thepresent invention is not limited to vehicles having an engine or motor.

A Preferred Embodiment

FIGS. 2 and 3 show a preferred embodiment of the present invention. FIG.2 is an exploded view of a preferred self-latching mechanism 200 to beused in the environment shown in FIG. 1, in place of reference number112 which represented a generic self-latching mechanism with a brakingmechanism.

The Latch Mechanism

Self-latching mechanism 200 is comprised of a pivot plate 202 which isattached to the top of a portable oil drain such as that shown asreference number 100 in FIG. 1. The pivot plate 202 is preferablyattached to the portable oil drain cover 115 by a number of conventionalfasteners such as a bolt 204 (mating nut and lock washer not shown) oralternatively a machine screw. The pivot plate 202 is shaped so that itincludes a tube channel which is preferably a cylindrical void 206 whichhas a diameter that is slightly larger than the diameter of the draintube 110 (FIG. 1) such that the drain tube 110 can slide axially throughthe cylindrical void 206 but is substantially constrained from lateralmovement within the cylindrical void 206. A protruding tube 210 on thebottom of the pivot plate 202 defines part of the cylindrical void 206.

Although the preferred embodiment is preferably a cylindrical drain tube110 and a corresponding cylindrical void 206, the present invention isnot limited to this combination. A conduit of any reasonable crosssection could be used including oblong, rectangular, or some combinationof the two. The tube channel need not have the same shape as the draintube 110. The function of allowing downward axial motion butsubstantially constraining lateral movement of the drain tube 110, couldbe achieved through use of a polygonal channel of appropriate dimension.As examples, the channel could be triangular, square, pentagonal, etcetera, or irregularly shaped with guide surfaces sufficient tosubstantially constrain the drain tube 110 from lateral movement.

The pivot plate 202 has a pivot mount 214 which is adapted to receive ahandle assembly 216 so that the handle assembly 216 can pivot around apivot axis 218. The hardware to mount the handle assembly 216 to thepivot plate 202 is a conventional bolt and nut assembly 219 and need notbe explained in any detail.

The handle assembly 216 in the preferred embodiment is made of a set ofwishbone arms 222 and 224. In the preferred embodiment these twowishbone arms 222 and 224 are identical, with such additional holes asare needed for the wishbone arms 222 and 224 be interchangeable.

Each of the two wishbone arms 222 and 224 has at least one slot 226which is sized and spaced on the wishbone arms 222 and 224 to receive aset of tabs 228 on a latch plate 230 having a curved leading edge 231.The two wishbone arms 222 and 224 are joined at the end opposite thebolt and nut assembly 219 by a handle piece 232. Thus the "wishbone" isformed with the proximal end of the wishbone in the handle piece 232 andthe two distal ends of the wishbone connected to the bolt and nutassembly 219.

FIG. 3 shows a top down view of a mounted handle assembly when thehandle assembly 216 is rotated to be in a horizontal position withrespect to the pivot axis 218. The latch plate 230 is sized andpositioned in the handle assembly 216 such that the leading edge 231 ofthe latch plate 230 slightly overlaps the cylindrical void 206. (Notethat drain tube 110 is not present in FIG. 3 so the over centerinterference can be more clearly illustrated.) Therefore, the latchplate 230 is capable of providing an interference fit when the draintube 110 is in place, so as to stop and hold the drain tube when thedrain bowl 108 (FIG. 1) is let go by the user after placing the drainbowl 108 in position for use under the vehicle. In the preferredembodiment, the leading edge 231 of the latch plate 230 is curved awayfrom the drain tube (110 in FIG. 1). Additionally, the latch plate 230is punched out of metal plate and positioned with the rounded edge fromthe punch process making contact with the drain tube (110 in FIG. 1).

The latch plate 230 is preferably mounted in a substantially fixedposition in the handle assembly 216. A substantially fixed latch plate230 with the leading edge 231 having a curved and rounded surfaceprovides a smooth engagement with the drain tube 110 when the userrotates the handle assembly 216 to engage or disengage the latchmechanism.

The Brake and the Brake Adjustment

As shown in both FIGS. 2 and 3, a threaded carriage bolt 234 and a wingnut 236 act as a brake adjustment to squeeze the two wishbone arms 222and 224 together around the drain tube 110. The square shoulder underthe head of the standard carriage bolt 234 engages with a square openingin the adjacent wishbone arm 224 to prevent the carriage bolt 234 fromrotating.

Other types of threaded elements could be used, preferably with lockwashers or some other bias against rotation, in place of the carriagebolt 234. Additionally, the wing nut 236 could be replaced by somealternative rotating element. The alternative rotating element could bea threaded shank which engages a threaded element which has a threadedbore.

Preferably the alternative rotating element is suitable for receivingtorque by hand rather than through use of a tool such as a wrench orscrewdriver.

Ideally, the rotating element is suitable for receiving torque by handthat is sufficient to alter the brake adjustment from a first extremeposition in which the brake provides virtually no impediment to downwardmovement of the drain tube 110 to a second extreme position in which thebrake adjustment causes the brake to impart sufficient frictionalresistance to hold a stopped drain tube 110 against the force of gravityacting on the drain tube 110 and the drain bowl 108 with its ordinarycontents. Note that the range of adjustment may extend substantiallybeyond one or both of the "extreme" positions. Additionally a devicecould be made in accordance with the present invention that does nothave a range of adjustment sufficient to reach both or even either"extreme" position.

In the preferred embodiment, a helical spring 238 is placed on thecarriage bolt 234 adjacent to the wing nut 236. Rotation of the wing nut236 alters the amount of compressive force which pushes the two wishbonearms 222 and 224 towards one another. With the drain tube 110 in thecylindrical void 206, the two wishbone arms 222 and 224 will notcontinue to move appreciably inward with increased tightening rotationof the wing nut 236 once the arms 222 and 224 are both in contact withthe outer edges of the drain tube 110. However, the resultant tighteningof the contact between the wishbone arms 222 and 224 and the drain tube110 produces an increasing friction force between the drain tube 110 andthe wishbone arms 222 and 224 to resist motion of the drain tube 110.Thus, when the handle assembly 216 is grasped by the user at the handlepiece 232 and rotated upward around the pivot axis 218, the leading edge231 of the latch plate 230 disengages from the surface of the drain tube110. When the latch plate 230 is disengaged from the drain tube 110, thedrain tube 110 is free to fall down through the cylindrical void 206 inthe pivot plate 202, impeded only by the friction force between thedrain tube 110 and the wishbone arms 222 and 224 that have beentightened around the drain tube 110 by the carriage bolt 234 and wingnut 236.

Therefore, the released drain tube 110 does not experience free fallacceleration; because the contact area between the two wishbone arms 222and 224 against the drain tube 110 serves as a motion-resisting brake.The released drain tube 110 accelerates downward at an accelerationsubstantially equal to the local acceleration of gravity minus the forceof the brake (and minus the effect of the lesser friction forces such asincidental contact with the cylindrical void 206).

Contingent on the length and arrangement of the drain tube 110 insidethe drain tank 114 and the level of the reservoir of waste oil 116 theremay be another significant friction force if the drain tube 110 has totravel through the reservoir of waste oil 116. The fluid resistance fromthe oil in the drain tank 114 adds another level of variability to thesystem which is another reason that the brake is preferably anadjustable brake.

The amount of friction force exerted by the brake is adjusted byrotation of the wing nut 236. Inclusion of the helical spring 238 servestwo purposes. The helical spring 238 makes for a more gradual increaseof friction force as the wing nut 236 is rotated in a tighteningdirection, thereby reducing the responsiveness of the wishbone arms 222and 224 to the rotation of the wing nut 236, so as to provide finercontrol of the braking force. Another spring present in the brakeadjustment is the elastic deformation of the two wishbone arms 222 and224. The deformation of the arms acts as a pair of springs to attenuatechanges in the applied frictional resistance due to rotation of therotating element.

The reaction force with which the helical spring 238 resists the wingnut 236 also serves the same function as a lock washer and frictionallyprevents undesired rotation of the wing nut 236.

Thus, the present invention provides a simple brake with a brakeadjustment that can be adjusted by hand to compensate for wear on thebrake surface, wear on the surface of the drain tube 110, the presenceof oil on the surface of the drain tube 110, or the added resistance todownward movement of the drain tube 110 from an elevated level of thereservoir of waste oil 116 in the drain tank 114. The brake adjustmentis also readily adjusted to compensate for individual preferences onrate of descent acceleration and speed. The brake adjustment iscontrolled by the rotating element, the wing nut 236, which isadvantageously positioned so that it can be adjusted with one hand whilethe other hand is maintaining the handle assembly 216 in the raisedposition to keep the latch plate 230 out of the way of the falling draintube 110.

The ability to adjust the brake control while the drain tube 110descends is useful in cases in which additional weight in the drain bowl108 would otherwise cause the drain tube 110 to descend faster thanpreferred by the user. Making such an adjustment while the drain tube110 descends would require use of both hands. However, unlike prior artdevices, a self-latching mechanism with a brake can be used with onehand to bring the heavy load down without achieving excessive speed.

For example, if a user leaves a heavy tool or an unusual number of oilfilters in the drain bowl 108, the drain bowl 108 will descend fasterthan usual. The frictional resistance, while less than desired for theheavy load will, however, still substantially restrain the accelerationand thus the maximum speed of the heavy load. Since the heavy load isnot in free fall, the user will have some time to release or move thehandle assembly 216 to stop the acceleration. Therefore, a series ofaccelerations held to a manageable level the braking force andterminated one or more times by movement of the handle assembly 216 tostop the drain tube 110 before it reaches bottom, can be used to bringeven an unusually heavy load down at an acceptable maximum speed whileusing only one hand.

In the event that the drain bowl 108 and the bowl contents are too lightto cause the drain tube 110 to descend against braking force that is setfor a much heavier load, the user can either readjust the braking forceor pull down on the drain bowl 108 with a free hand.

Other Embodiments

After disclosure of this preferred embodiment, one skilled in the artcould make a number of substitutions and variations in keeping with theteachings of the present invention to add a friction brake to aself-latching mechanism. FIG. 4 shows one such variation.

FIG. 4 shows a top down view of an alternate embodiment of theself-latching mechanism 250. To highlight the differences with thepreferred embodiment, only the parts which are necessary to explain thedifferences are identified in FIG. 4. To further emphasize thedifferences between the two embodiments, elements of the alternateembodiment which are different from the preferred embodiment are givennew reference numbers. For example, FIG. 4 contains reference number 250instead of reference number 200 for the self-latching mechanism.

The principal difference in FIG. 4 is the use of a floating latch plate252 with a circular cut-out 254. This floating latch plate 252 is usedin place of latch plate 230 (FIG. 2). The drain tube 110 (FIG. 1) isplaced through the cut-out 254 and into the cylindrical void 206 (FIG.2). The drain tube 110 can pass through the cut-out 254 when theself-latching mechanism 250 is rotated up toward the horizontalorientation of the floating latch plate 252 so that horizontal distancebetween a distal edge 256 of the cut-out 254 and a proximal edge 258 ofthe cut-out 254 exceeds the outer diameter of the drain tube 110.Rotation of the self-latching mechanism 250 downward from the horizontalorientation of the floating latch plate 252 reduces the horizontaldistance between the two edges 256 and 258. The rotation downwardcontinues until the two edges 256 and 258 pinch the drain tube 110, tostop and hold the drain tube 110.

The maximum clearance for the vertical drain tube 110 to pass through agiven cut-out is present when the cut-out walls are aligned parallelwith the drain tube 110 walls. Thus, if the cut-out 254 is alignednormal to the surface of the floating latch plate 252, the horizontaldistance between the two edges 256 and 258 will be greatest when thefloating latch plate 252 is horizontal. Thus, the handle piece 232 musthave room to fall below horizontal so that the floating latch plate 252can rotate to pinch and hold the wall of the drain tube 110.

The use of a cut-out aligned at an oblique angle relative to the surfaceof the floating latch plate 252 results in maximum clearance when thefloating latch plate 252 is rotated to the angle that vertically alignsthe cut-out wall. This is illustrated in FIG. 5 where a side view ofalternative floating latch plate 270 is shown with a floating latchplate tab 272 in the foreground. The position of an oblique cut-out 274is indicated by the dashed lines. To emphasize the effect of the obliqueangle, the angle has been illustrated at a exaggerated deviation fromnormal to the floating latch plate 270. Additionally, the thickness ofthe floating latch plate 270 has been exaggerated to emphasize theeffect of the oblique angle for the cut-out 274. Notice that theclearance space for a drain tube 110 (FIG. 1) is limited by thehorizontal distance between a leading distal edge 276 of the obliquecut-out 274 and a leading proximal edge 278 of the oblique cut-out 274.Thus, the use of a cut-out aligned at an oblique angle can be used toalter the angles at which the floating latch plate pinches and releasesthe drain tube.

The floating latch plate 252 or 270 with a cut-out (either normal oroblique) can be used with the present invention but is not the preferredmode. The reason that the latch plate 230 is preferred over floatinglatch plates 252 or 270 is the simple rotational movement of the latchplate 230 as constrained from translational movement by the constraintof the set of tabs within the slots 226. The constraint provides asmoother operation of the latch mechanism than is found in the alternateembodiment. In the alternative embodiment shown in FIG. 4 the movementof the floating latch plate 252 is a combination of rotational andtranslational movement.

FIG. 4 has a partial cutaway of the alternative wishbone arms 260 toshow the position of a set of tabs 262 for alternative floating latchplate 252 resting on the bottom edge of one of the two slots 264. (Theother slot cannot be seen in this view but is located in thecorresponding position in the other wishbone arm.) The slots 264 aresized so that the tabs 262 do not contact the end of the slots 264 toconstrain the movement of the floating latch plate 252 from movementalong the length of the slots 264 within the wishbone arms 260. Theslots 264 and set of tabs 262 are sized to allow the floating latchplate 252 to move until rotation of the floating latch plate 252 pinchesthe drain tube 110 (FIG. 1).

The movement of the floating latch plate 252 in the wishbone arms 260accentuates the bipolar bind and release behavior of the latchingmechanism. At least some users prefer the roll-on/roll-off sensationprovided by the preferred self-latching mechanism 200 over the bitingsensation of the alternate self-latching mechanism 250.

FIGS. 6,7, and 8 illustrate another embodiment of the present invention.A floating latch plate 300 is shown in FIG. 6 and FIG. 7 but omittedfrom FIG. 8 to provide a view of other elements. The floating latchplate 300 has the cut-out 254, distal edge 256, and proximal edge 258described in the text associated with FIGS. 4 and 5. The floating latchplate 300 is not connected to a pivot axis (compare 218 in FIG. 4) butoperates to release the drain tube 110 when the user raises floatinglatch plate handle 302 to cause a combination of rotational movement andtranslational movement of the floating latch plate 300 to align thecut-out 254 with the drain tube 110 to allow the drain tube 110 to drop.The rotational movement of the floating latch plate 300 will arise fromthe pivoting of the floating latch plate 300 relative to a floatinglatch plate support 304. The floating latch plate support 304 isconnected to a pivot plate 306 using some of a set of fasteners 204 usedto connect the pivot plate 306 to a drain tank cover 308. (Shown here inmore detail than cover 115 in FIG. 1.)

Release of the floating latch plate handle 302 causes the floating latchplate 300 to fall and grab the drain tube 110 with a pinching engagementas previously discussed. Note that the slope of a top surface 310 of thefloating latch plate support 304 must be designed to allow the floatinglatch plate 300 to rotate into pinching engagement with the drain tube110. It is better to provide the top surface 310 with enough slope sothat the floating latch plate 300 cannot rotate down to contact theentire top surface 310, (as shown in FIG. 6) than to provide aninadequate slope and stop rotation of the floating latch plate 300before pinching engagement stops the drain tube 110.

FIG. 8 presents a top view of this embodiment with the floating latchplate 300 removed. In addition to previously identified elements, FIG. 8shows the elements in the brake mechanism for the present embodiment.The present embodiment provides a motion resisting contact area toresist downward motion of the drain tube 110 by positioning a wedgeshaped object 320 into contact with the drain tube 110. The drain tube110 is constrained from lateral movement by the cylindrical void (shownin FIG. 2 element 206) and the inside wall of the floating latch platesupport 304 that is positioned in contact with the drain tube 110 overabout 180 degrees of its circumference. The amount of frictionalresistance to downward motion is altered by rotation of a thumbscrew322.

Thumbscrew 322 is shown in greater detail in FIG. 9 in which thefasteners 204 have been omitted to promote clarity. The thumbscrew 322is comprised of a thumbpiece 324, and a shank 326. The majority of theshank 326 is smooth, but the shank 326 has a threaded portion 328 at theend distal to the thumbpiece 324. A threaded element 330 having athreaded bore (not shown) is associated with one side of the floatinglatch plate support 304. The threaded element 330 shown in thisembodiment is a nut that has been tack welded adjacent to and alignedwith an opening in the floating latch plate support 304. The threadedelement could be a threaded bore in floating latch plate support 304,but that would require a thicker metal piece for fabrication of thefloating latch plate support 304.

The wedge shaped object 320 is shown here is a sleeve for the shank 326in the shape of truncated cone. Other shapes could be used as well,including an elongated polyhedron that approximates a truncated cone oreven an elongated polyhedron that has several parallel faces and onenon-parallel face that extends out toward the drain tube 110.

The wedge shaped object 320 is held in place on the shank 326 by a pairof axial stops 332. The axial stops 332 shown here are spring washerswhich prevent axial movement of the wedge shaped object 320 relative tothe shank 326. Another common axial stop (not shown) is known as an"E-clip". One skilled in the art of machine design could substituteother axial stops including an application of glue or a bead of welding.Note that the shank 326 can rotate within a bore shaped void 334 (shownhere via a partial cutaway) in the wedge shaped object 320, but rotationof the thumbscrew 322 will cause axial motion of the wedge shaped object320 such that the wedge shape presses less or more against the draintube 110 so as to alter the frictional force on the drain tube 110 andthe surface of the support 304 that is wrapped 180° around the draintube 110.

Note that although the brake mechanism of this embodiment is illustratedin combination with a particular floating latch plate 300, the brakemechanism operates independently of the latch mechanism. This brakemechanism could be adapted for use with any latch mechanism includinglatch mechanisms that are part of a pivotally mounted handle assembly.

FIGS. 10, 11, 12, and 13 show another embodiment of the presentinvention. FIGS. 10 and 11 show the embodiment in the latched position.FIGS. 12 and 13 show the embodiment in the unlatched position. The draintube 110 also passes through the cylindrical void (FIG. 2 element 206)in the pivot plate 202 which is attached to the drain tank cover 308.The drain tube 110 passes through a handle assembly comprised of a pairof handle arms 400 with the distal ends of both handle arms pivotallymounted on a bolt and nut assembly 219 passing through ears in the pivotplate 202 (See FIG. 2 and related text for more detail on bolt and nutassembly 219.) The two distal ends of the handle arms 400 are keptsubstantially adjacent to one another by a pair of spacers 402 that aremounted on the bolt and nut assembly 219. The proximal ends of bothhandle arms 400 are joined by a handle piece 232.

Note that the shape of the handle arms 400 forms a wedge shaped void404. When the handle assembly is rotated down to horizontal, the portionof the handle arms 400 containing the wedge shaped void 404 moveshorizontally toward the drain tube 110 and engages the drain tube 110 towedge the drain tube 110 between the two handle arms 400. The spacers402 resist the tendency of the distal ends of the handle arms 400 toexpand the wedge shaped void 404.

FIG. 12 shows the handle assembly raised to the unlatched position. Asbest shown in FIG. 13, rotation of the handle arms 400 to the unlatchedposition causing the wedge shaped void 404 to move away from the draintube 110 (which appears elliptical in FIG. 13 because the view is takenat an angle relative to the circular cross section of the drain tube110). Once free of the binding effect of the portion of the handle arms400 that form the wedge shaped void 404, the drain tube 110 facesfrictional resistance to downward motion from a motion resisting contactarea in which the drain tube 110 contacts the inner walls of the handlearms 400. The amount of frictional resistance is regulated by a threadedassembly 233 made up of the carriage bolt 234, wing nut 236, and helicalspring 238.

Placement of the threaded assembly 233 toward the handle piece 232rather than closer to the drain tube 110 provides a greater moment armfor the threaded assembly 233 which reduces the effect of rotating thewing nut 236 by a small amount. This reduced response to a given amountof rotation provides an increase in the amount of control over theresistance to motion. A longer handle assembly could be used to give aneven longer moment arm. Also, the inevitable flexibility of the handlearms 400 further reduces the frictional response to a given rotation ofthe wing nut 236.

Yet another embodiment of the present invention is illustrated in FIGS.14 and 15. The braking mechanism is similar to that shown in some of thepreceding embodiments. Control of the frictional force is by rotation ofrotating element (the wing nut 236) that is threadedly mounted on thethreaded element (the carriage bolt 234). Rotation of the wing nut 236compresses a pair of handle arms 500 to squeeze the drain tube 110 toresist downward motion of the drain tube 110. The optional helicalspring 238 attenuates the change in frictional resistance for a givenamount of rotation of the wing nut 236. Note that this embodiment placesthe threaded assembly 233 on the opposite side of the drain tube 110from the handle piece 232.

In this embodiment, the threaded assembly passes through the pair ofhandle arms 500 and through a pivot mount 502. Note that the pivot mount502 does not abut the pair of handle arms 500, thus allowing room forcompression of the gap between the pair of handle arms 500 and the pivotmount 502 at the threaded assembly 233. Pivot mount 502 abuts the draintube 110 to add an additional restraint against lateral movement of thedrain tube 110.

The latch mechanism of this embodiment relies on the force imparted by aball 504 that applies pressure against the drain tube 110 to press thedrain tube 110 against the cylindrical void (FIG. 2, element 206) andthe fixed wall of the pivot mount 502.

The movement of the ball 504 is substantially constrained by a fixedelement 506 having a concave channel. As shown best in FIG. 14, thefixed element 506 has a U-shaped bracket which is open to the ball 504.The fixed element 506, like the pivot mount 502, is mounted by fasteners204 to the pivot plate 202 and the drain tank cover 308 (shown in FIG.15). As best seen in the partial cutaway in FIG. 15, the fixed element506 has a sloped face so that the bottom of the fixed element 506 iscloser to the drain tube 110 than is the top of the fixed element 506.

The ball 504 is further constrained by an upper restraining element 508and a lower restraining element 510. In the present embodiment both arepins which pass through holes in the pair of handle arms 500 and areeither locked in place by spring clips 512, tack welded to the pair ofhandle arms 500, or affixed to the handle arms 500 in some other manner.

The operation of the latch is as follows. Lifting the handle piece 232causes the pair of handle arms 500 to rotate up around the threadedassembly 233 which passes through the pivot mount 502. The lowerrestraining element 510 moves with the pair of handle arms 500 andpushes up on the ball 504. As the ball 504 moves up, there is moreclearance for the ball 504 between the fixed element 506 and the draintube 110. After the ball 504 moves sufficiently, the drain tube 110 isreleased to fall downward, impeded only by the frictional resistanceimparted by the action of the carriage bolt 234 to bias the inner wallsof the pair of handle arms 500 against the drain tube 110. The upperrestraint 508 serves to keep the ball 504 from coming out of theconstrained area.

Release of the handle piece 232 causes the pair of handle arms 500 torotate down under the force of gravity. Gravity and pressure from theupper restraint 508 push the ball downward along the channel defined bythe fixed element 506. The channel defined by the fixed element 506leads the ball 504 into contact with the drain tube 110. The downwardmovement of the drain tube 110 causes the ball 504 to move further downinto the decreasing gap between the fixed element 506 and the drain tube110, until the drain tube 110 is bound between the ball 504 and thecombination of the pivot mount 502 and the walls of the cylindrical void(FIG. 2, element 206).

The conception and the specific embodiments disclosed above may bereadily utilized as a basis for modifying other structures for carryingout the purposes of the present invention. Such equivalent constructionsdo not depart from the spirit and scope of the invention, as set forthin the appended claims.

I claim:
 1. A brake for a vehicle fluid drain unit comprising a drain tube supporting a vehicle fluid drain bowl, the brake comprising:a motion resisting contact area for contact with the drain tube to impart frictional resistance to the downward movement of the drain tube, comprising:a first motion resisting surface; and a second motion resisting surface located on substantially the opposite side of the drain tube from the first motion resisting surface; the first motion resisting surface and the second motion resisting surface being capable of being biased relative to one another to squeeze the drain tube to restrain the downward motion of the drain tube; and a brake adjustment for adjusting the frictional resistance imparted by the motion resisting contact area to the drain tube.
 2. The brake of claim 1 wherein the brake adjustment comprises:a threaded assembly associated with the motion resisting contact area, the threaded assembly comprising a threaded element and a rotating element threadedly engaged with the threaded element; the brake adjustment adapted to alter the frictional resistance by rotation of the rotating element with respect to the rest of the threaded assembly to cause the threaded assembly to act upon the motion resisting contact area.
 3. The brake of claim 2 wherein the threaded assembly is adapted to convert rotation of the rotating element into biasing of the second motion resisting surface relative to the first motion resisting surface to alter the frictional resistance imparted by the motion resisting contact area to the drain tube.
 4. The brake of claim 3 wherein the second motion resisting surface is part of a wedge which is moved linearly by the rotation of the rotating element and the wedge is positioned to alter the frictional resistance.
 5. The brake of claim 4 wherein the wedge defines a void and the threaded element passes through the void and the brake further comprises an axial stop mounted on the threaded element adjacent to the wedge void to limit the axial movement of the wedge relative to the threaded assembly, the axial stop moving axially with the rotation of the rotating element to move the wedge axially.
 6. The brake of claim 5 wherein the brake further comprises a second axial stop mounted on the threaded element adjacent to the wedge void.
 7. The brake of claim 4 wherein the rotation element is a thumbscrew with a thumbpiece and a shank, the shank having a set of threads on a portion of the shank distal to the thumbpiece, the wedge and the axial stops placed over unthreaded portions of the shank.
 8. The brake of claim 2 wherein the brake adjustment further comprises a spring associated with the threaded assembly and the motion resisting contact area,the spring attenuating the alteration of the frictional resistance in response to rotation of the rotating element.
 9. The brake of claim 8 wherein the spring is a structure elastically deformed by the threaded assembly during rotation of the rotating element.
 10. The brake of claim 9 wherein the spring is an arm connecting the motion resisting contact area to the threaded assembly, the rotation of the rotating element causing elastic deformation of the arm.
 11. The brake of claim 2 wherein the threaded assembly further comprises a helical spring, the helical spring positioned to surround a portion of the threaded assembly, the helical spring adapted to be compressed during rotation of the rotating element.
 12. The brake of claim 2 wherein the motion resisting contact area is a part of a sleeve that is associated with the rotating element.
 13. The brake of claim 1 wherein the brake adjustment has:a first position wherein the first motion resisting surface and the second motion resisting surface are biased relative to one another to hold the drain tube fixed against the force of gravity; a second position wherein the drain tube falls substantially unimpeded by the motion resisting surfaces; and a range of positions between the first position and the second position whereby the downward acceleration of the stopped drain tube can be selectively varied from zero to substantially the local acceleration of gravity.
 14. The brake of claim 13 wherein the brake adjustment comprises:a threaded assembly associated with the motion resisting contact area, the threaded assembly comprising a threaded element and a rotating element threadedly engaged with the threaded element; the brake adjustment adapted to alter the frictional resistance by rotation of the rotating element with respect to the rest of the threaded assembly to cause the threaded assembly to act upon the motion resisting contact area.
 15. The brake of claim 14 wherein the rotating element is adapted to receive torque directly from a human hand in sufficient magnitude to adjust the brake adjustment from the second position to the first position.
 16. The brake of claim 15 wherein the rotating element is a wing nut and the threaded element comprises a shank that is threaded along at least a portion of the length of the shank.
 17. The brake of claim 15 wherein the rotating element is a thumbscrew and the threaded element defines a threaded bore.
 18. The brake of claim 15 wherein the brake adjustment further comprises a spring associated with the threaded assembly and the motion resisting contact area to reduce the alteration of the frictional resistance in response to rotation of the rotating element.
 19. A braking system for a vehicle fluid drain unit, the vehicle fluid drain unit comprising a vehicle fluid drain bowl, a plate with a channel wall defining a tube channel, and a drain tube supporting the vehicle fluid drain bowl, the drain tube aligned substantially vertically and passing substantially vertically through the tube channel defined by the channel wall, the channel wall substantially constraining the lateral movement of the drain tube, the brake system comprising:a latch mechanism to hold the drain tube against the force of gravity; a motion resisting contact area for contact with the drain tube to impart frictional resistance to the downward movement of the drain tube, comprising:a first motion resisting surface; and a second motion resisting surface located on substantially the opposite side of the drain tube from the first motion resisting surface; the first motion resisting surface and the second motion resisting surface being capable of being biased relative to one another to squeeze the drain tube to restrain the downward motion of the drain tube; and a brake adjustment for adjusting the frictional resistance applied by the motion resisting contact area to the drain tube.
 20. The braking system of claim 19 wherein the latch mechanism comprises:a pivot mount adapted to be connected to the vehicle fluid drain unit; a handle assembly pivotably mounted on the pivot mount; a latch plate adapted to engage the surface of the drain tube upon pivoting rotation of the handle assembly about the pivot mount to hold the drain tube and supported vehicle fluid drain bowl against the force of gravity.
 21. The braking system of claim 20 wherein the latch plate is adapted to engage the drain tube in an interference fit to hold the drain tube and supported vehicle fluid drain bowl against the force of gravity.
 22. The braking system of claim 21 wherein the latch mechanism is a self-latching mechanism adapted to engage the drain tube when the drain tube moves downward.
 23. The braking system of claim 22 wherein the latch mechanism is disengaged to release the drain tube by rotation of the handle assembly about the pivot mount.
 24. The braking system of claim 20 wherein the motion resisting contact area is associated with the handle assembly.
 25. The braking system of claim 24 wherein the brake adjustment is connected to the handle assembly such that the brake adjustment pivots with the handle assembly around the pivot mount.
 26. The braking system of claim 20 wherein the latch plate is substantially fixed in the handle assembly such that the position of the latch plate is substantially constant for a given degree of rotation of the handle assembly about the pivot mount.
 27. The braking system of claim 20 wherein the latch plate is attached to the handle assembly by at least two latch tabs in slotted engagement with the handle assembly.
 28. The braking system of claim 19, wherein the latch mechanism comprises:a floating latch plate having inner walls which define a cut-out void of sufficient size to allow axial travel of the drain tube through the cut-out void for at least some orientations of the cut-out void relative to the drain tube; a latch plate mounting means to connect the floating latch plate to the vehicle fluid drain unit to allow both rotation and translation of the floating latch plate;the latch plate mounting means comprising at least one sliding engagement with the latch plate to allow translational motion of the latch plate relative to the latch plate mounting means; a support which allows the floating latch plate to rotate around the support; a fixed piece which connects the latch plate mounting means to the vehicle fluid drain unit, the floating latch plate further comprising a leading edge proximal to the fixed piece and a leading edge distal to the fixed piece and a horizontal distance between the two leading edges, the movement of the floating latch plate in a combination of rotation and translation causing a reduction in the horizontal distance between the two leading edges to cause a pinching engagement between the two leading edges and the drain tube sufficient to hold the drain tube against the force of gravity.
 29. The braking system of claim 28 wherein the latch mechanism is a self-latching mechanism adapted to engage when the drain tube moves downward.
 30. The braking system of claim 29 wherein the latch mechanism further comprises a latch release, and an upward force on the latch release disengages the pinching engagement between the two leading edges and the drain tube to the release the drain tube.
 31. The braking system of claim 28 wherein the brake adjustment comprises:a threaded assembly, the threaded assembly comprising a threaded element and a rotating element threadedly engaged with the threaded element; the brake adjustment adapted to alter the frictional resistance by a rotation of the rotating element with respect to the threaded element.
 32. The braking system of claim 19 wherein the latch mechanism comprises:a floating latch plate having inner walls which define a cut-out void of sufficient size to allow axial travel of the drain tube through the cut-out void for at least some orientations of the cut-out void relative to the drain tube, the floating latch plate further comprising a latch plate handle; a floating latch plate support to limit the downward travel of the floating latch plate toward the plate;the floating latch plate further comprising: a leading edge proximal to the floating latch plate handle; a leading edge distal to the floating latch plate handle; and a horizontal distance between the two leading edges; the downward movement of the floating latch plate in a combination of rotational movement and translational movement causing a reduction in the horizontal distance between the two leading edges to cause a pinching engagement between the two leading edges and the drain tube sufficient to hold the drain tube against the force of gravity; the floating latch plate further adapted to release the drain tube upon sufficient upward movement of the floating latch plate handle.
 33. The braking system of claim 32 wherein the brake adjustment comprises:a threaded assembly, the threaded assembly comprising a threaded element and a rotating element threadedly engaged with the threaded element; the brake adjustment adapted to alter the frictional resistance by a rotation of the rotating element with respect to the threaded element.
 34. The brake of claim 33 wherein the motion resisting contact area comprises:a first motion resisting surface; and a second motion resisting surface located on substantially the opposite side of the drain tube from the first motion resisting surface, the threaded assembly connected to the second motion resisting surface to convert rotation of the rotating element into movement of the second motion resisting surface relative to the first motion resisting surface to alter the frictional resistance.
 35. The brake of claim 34 wherein the second motion resisting surface is part of a wedge which is moved linearly by the rotation of the rotating element and the wedge is positioned to alter the frictional resistance.
 36. The braking system of claim 32 wherein the latch mechanism is a self-latching mechanism adapted to engage when the drain tube moves downward.
 37. The braking system of claim 19 wherein the latch mechanism comprises:a pivot mount; a handle assembly pivotably mounted on the pivot mount; a portion of the handle assembly between the pivot mount and the drain tube that defines a wedge shaped void, the wedge shaped void adapted to engage with the drain tube when the handle assembly is rotated down towards horizontal to a first position, and further adapted to provide unimpeded clearance for the drain tube when the handle assembly is rotated up from horizontal to a second position.
 38. The braking system of claim 37 wherein the handle assembly comprises:a first handle arm having a proximal end and a distal end, the distal end pivotally mounted to the pivot mount; a second handle arm having a proximal end and a distal end, the distal end pivotally mounted to the pivot mount; and a handle piece connecting the proximal end of the first handle arm and the proximal end of the second handle arm.
 39. The braking system of claim 38 wherein the handle assembly is adapted so that the distal end of the first handle arm is substantially adjacent to the distal end of the second handle arm.
 40. The braking system of claim 39 wherein the pivot mount further comprises two spacer elements and the placement of the two substantially adjacent distal ends of the two handle arms between the two spacer elements in the pivot mount is adapted to resist expansion of the wedge shaped void during engagement of the wedge shaped void and the drain tube.
 41. The braking system of claim 40 wherein the motion resisting contact area is associated with at least one of the two handle arms and the brake adjustment comprises:a threaded assembly having a threaded element and a rotating element threadedly engaged with the threaded element; and the brake adjustment being adapted to alter the frictional resistance by a rotation of the rotating element with respect to the threaded element.
 42. The braking system of claim 19 wherein the latch mechanism comprises:a ball; a first fixed element fixedly connected to the plate and having a sloped face adapted to guide the ball downward and toward the drain tube when the ball is suitably constrained; a means for lifting the ball from: a first position where the ball exerts sufficient force upon the drain tube to hold the drain tube against the force of gravity to a second position where the ball presents no substantial impediment to motion of the drain tube downward.
 43. The braking system of claim 42 wherein the first fixed element further comprises a concave channel in the sloped face to limit the lateral movement of the ball as it moves downward and toward the drain tube.
 44. The braking system of claim 43 wherein the means for lifting the ball comprises:a pivot mount; a handle assembly pivotably mounted on the pivot mount; the handle assembly comprising a first handle arm having a proximal end and a distal end, the distal end pivotally mounted to the pivot mount; a second handle arm having a proximal end and a distal end, the distal end pivotally mounted to the pivot mount; a handle piece connecting the proximal end of the first handle arm and the proximal end of the second handle arm; an upper restraining element substantially fixed between the first handle arm and the second handle arm; a lower restraining element substantially fixed between the first handle arm and the second handle arm, the position of the upper and lower restraining elements being adapted to push the ball along a path substantially constrained by the concave channel and the drain tube from the first position to the second position.
 45. The braking system of claim 44 wherein the motion resisting contact area is associated with one of the two handle arms.
 46. The braking system of claim 45 wherein the brake adjustment comprises:a threaded assembly having a threaded element and a rotating element threadedly engaged with the threaded element; and the brake adjustment being adapted to alter the frictional resistance by a rotation of the rotating element with respect to the threaded element.
 47. The braking system of claim 46 wherein the threaded assembly is used to pivotally mount the handle assembly.
 48. The braking system of claim 44 wherein the latch mechanism is a self-latching mechanism adapted to engage when the drain tube moves downward.
 49. The braking system of claim 44 wherein the upper restraining element and the lower restraining element are pins.
 50. The braking system of claim 44 wherein the latch mechanism further comprises a second fixed element fixedly mounted to the plate and substantially adjacent to the drain tube to exert binding force against the drain tube when the handle assembly is rotated to the second position.
 51. The braking system of claim 19 wherein the latch mechanism comprises:a pivot mount adapted to be connected to the vehicle fluid drain unit; a handle assembly pivotally mounted on the pivot mount, the handle assembly comprising:a first handle arm having a proximal end and a distal end, the distal end pivotally mounted to the pivot mount; a second handle arm having a proximal end and a distal end, the distal end pivotally mounted to the pivot mount; and a handle piece connecting the proximal end of the first handle arm and the proximal end of the second handle arm; the motion resisting contact area being associated with at least one of the two handle arms.
 52. The brake of claim 51 wherein the brake adjustment comprises:a threaded assembly having a threaded element and a rotating element threadedly engaged with the threaded element; and the brake adjustment being adapted to alter the frictional resistance by a rotation of the rotating element with respect to the threaded element.
 53. The brake of claim 52 wherein said brake adjustment further comprises a spring which is a structure resiliently compressed by the action of the threaded element.
 54. The brake of claim 53 wherein the spring is an arm connecting the motion resisting contact area to the threaded assembly.
 55. The brake of claim 54 wherein the latch mechanism further comprises a latch plate adapted to engage the surface of the drain tube upon pivoting rotation of the handle assembly about the pivot mount to hold the drain tube and supported vehicle fluid drain bowl against the force of gravity.
 56. A superstructure for a vehicle fluid drain unit for use in capturing fluid draining down out of a vehicle and draining the captured fluid to a fluid collection reservoir, the superstructure comprising:a drain bowl oriented and adapted to catch fluids draining from the vehicle, a drain tube adapted to support the drain bowl, and providing a fluid channel from the drain bowl toward the fluid collection reservoir, latch means for selectively holding the drain tube in a fixed elevated position against the force of gravity acting on the drain tube, the drain bowl and the contents of the drain bowl; the latch means comprising a latch release for selectively releasing the drain tube from the hold of the latch means; and brake means to resist the downward motion of the released drain tube, the brake means comprising:a first motion resisting surface; and a second motion resisting surface located on substantially the opposite side of the drain tube from the first motion resisting surface; the first motion resisting surface and the second motion resisting surface being capable of being biased relative to one another to squeeze the drain tube to restrain the downward motion of the drain tube.
 57. A method of draining vehicle fluid from a vehicle, into a drain bowl mounted on a drain tube movable relative to a fluid chamber comprising:a) placing the drain bowl and drain tube under the vehicle drain; b) raising the drain bowl with the drain tube to a first position closely spaced from and below the vehicle drain; c) latching the drain tube to hold the drain bowl to said first position; d) draining the vehicle fluid from the vehicle drain tube into the drain bowl; e) releasing the drain tube to permit the drain bowl and drain tube to retract from the first position to a second position vertically remote from the vehicle drain; and f) applying a braking force to the drain tube to limit the acceleration of the drain bowl and drain tube as the drain tube retracts from the first position, said braking force being created by squeezing the drain tube between two motion resisting surfaces.
 58. The method of draining a fluid from a vehicle in claim 57 further including the step of adjusting the braking force through manipulation of a brake adjustment.
 59. The method of draining a fluid from a vehicle in claim 58 wherein the step of adjusting the braking force is performed before releasing the latched drain tube.
 60. The method of draining a fluid from a vehicle in claim 59 wherein the step of adjusting the braking force is performed while the drain bowl with its drain tube is in the second position.
 61. The method of draining a fluid from a vehicle in claim 58 wherein the step of adjusting the braking force is performed during retraction of the drain tube from the first position.
 62. The method of draining a fluid from a vehicle in claim 58 wherein the step of adjusting the braking force is performed by a rotation of a rotating element.
 63. The method of draining fluid from a vehicle in claim 57 wherein the step of latching the drain tube to hold the drain bowl at said first position comprises letting go of the drain bowl to allow the drain bowl to fall slightly to engage a self-latching mechanism. 